EP3568574A1

EP3568574A1 - Turbine ring assembly

Info

Publication number: EP3568574A1
Application number: EP18700942.8A
Authority: EP
Inventors: Clément Jean Pierre DUFFAU; Sébastien Serge Francis CONGRATEL; Lucien Henri Jacques QUENNEHEN; Nicolas Paul TABLEAU
Original assignee: Safran Aircraft Engines SAS
Current assignee: Safran Aircraft Engines SAS
Priority date: 2017-01-12
Filing date: 2018-01-05
Publication date: 2019-11-20
Anticipated expiration: 2038-01-05
Also published as: US20190383166A1; FR3061738B1; CN110177923A; CA3050016A1; US11149586B2; CN110177923B; FR3061738A1; WO2018130766A1; EP3568574B1

Abstract

The invention relates to a turbine ring assembly comprising a plurality of ring sections (10) consisting of a composite material with a ceramic matrix forming a turbine ring (1) and a ring-supporting structure (3), each section (10) having, in a first section plane defined by an axial direction (D_A) and a radial direction (D_R) of the ring (1), a part forming an annular base (12) with, in the radial direction (D_R), an inner face (12a) and an outer face (12b) from which two fastening lugs (14, 16) extend, said lugs defining a peripherally open annular cavity (120), said structure (3) comprising two radial lugs between which the fastening lugs (14, 16) are held, and at least one opening (4) for the injection of a cooling air stream into the annular cavity (120). In a second section plane comprising the axial direction (D_A) and a direction (D_c) which is orthogonal to the first section plane (I), said opening (4) forms a first supply angle (α₁) of between -80° and +80° with said direction (D_c) which is orthogonal to the first section plane (I).

Description

Turbine ring assembly

Background of the invention

The invention relates to a turbine ring assembly comprising a plurality of ceramic matrix composite material ring sectors and a ring support structure, also known as a housing.

The field of application of the invention is in particular that of aeronautical gas turbine engines. The invention is however applicable to other turbomachines, for example industrial turbines.

In the case of all-metal turbine ring assemblies, it is necessary to cool all the elements of the assembly and in particular the turbine ring which is subjected to the hottest flows. This cooling has a significant impact on the engine performance since the cooling flow used is taken from the main flow of the engine. In addition, the use of metal for the turbine ring limits the possibilities of increasing the temperature at the turbine, which would however improve the performance of aircraft engines.

In an attempt to solve these problems, it has been envisaged to produce turbine ring sectors made of ceramic matrix composite material (CMC) in order to overcome the implementation of a metallic material.

CMC materials have good mechanical properties making them suitable for constituting structural elements and advantageously retain these properties at high temperatures. The use of CMC materials has advantageously made it possible to reduce the cooling flow to be imposed during operation and thus to increase the performance of the turbomachines. In addition, the use of CMC materials advantageously makes it possible to reduce the weight of the turbomachines and to reduce the effect of hot expansion encountered with the metal parts.

However, the CMC materials are very stiff and have a low mechanical permissible compared to the metal alloys traditionally used. In addition, in a gas turbine engine, the high pressure turbine ring is confronted with a hot source, the vein, and a cold source which is the cavity between the ring and the housing, hereinafter called " cavity ring ".

Indeed, the ring cavity must be at a pressure greater than that of the vein to prevent the air from the vein can go up and come burn the metal parts. This overpressure is obtained by drawing air at the compressor and bringing it into the ring cavity, which explains why this air is "cold" since it is not heated in the combustion chamber.

This need for overpressure makes it impossible to completely cut off the "cold" air supply of the ring cavity and thus impossible to remove the cold source. It is therefore impossible to have a ring with a homogeneous temperature. Therefore, there will be significant thermal gradients, which will generate mechanical stresses in the ring.

Studies have shown that it is necessary to have the most radial thermal gradient possible, that is to say to have the lowest possible axial and tangential thermal gradients.

A known technique for optimizing the cooling of the ring cavity is to make the impact: the cooling air passes through a multi-perforated sheet, which accelerates and increases the exchange coefficients with the screw surface vis-à-vis, which corresponds, in this case, to the upper face of the ring. This allows, with the same temperature and the same rate of cooling air, to cool more effectively an area of the ring.

However, it is necessary to force the passage of air through this sheet. Otherwise, the air will not go through the holes and the cooling will be ineffective. On a metal ring, this is achieved by means of a weld on the periphery of the ring.

Transposing this ring technology to CMC is impossible for two reasons.

Firstly, the coefficient of expansion between a metal sheet and a CMC ring is too great. The two pieces will deform too differently to maintain and seal over time. Secondly, it is impossible to weld parts made of CMC material. The multi-perforated sheet could have been made in CMC to overcome the difficulty of the first point. However, there is currently no technique for welding / brazing one CMC part with another.

One solution is to exploit the flow of air in the ring cavity and to make it work "intelligently" so as to attenuate the axial and azimuth gradients. For this, a known technique is to tilt the feed holes of the ring cavity to induce a swirl effect, or "swirl" in English, and increase the exchange coefficients and the cooling efficiency on the pad of the 'ring.

This solution is not adaptable to the turbine rings present on the engines, because the presence of walls at each annular ring portion end makes the ring cavity is not symmetrically symmetrical, and does not allow to introduce of global rotating flow in the cavity, that is why the feed holes are now purely axial.

Object and summary of the invention

The aim of the invention is to provide a turbine ring assembly comprising a composite matrix ceramic ring that provides an injection of an air flow into the ring cavity that eliminates the axial temperature gradient.

An object of the invention provides a turbine ring assembly comprising a plurality of ceramic matrix composite ring sectors forming a turbine ring and a ring support structure, each ring sector having, according to a first section plane defined by an axial direction and a radial direction of the turbine ring, an annular base portion with, in the radial direction of the turbine ring, an inner face defining the inner face of the ring turbine and an outer face from which extend a first and a second attachment tabs defining between them a circumferentially open annular cavity, the ring support structure having a first and a second radial tabs between which are maintained the first and second attachment tabs of each ring sector, and at least one injection port for a cooling air flow in the annular cavity.

According to a general characteristic of the invention, in a second section plane comprising the axial direction of the ring and a direction orthogonal to the first section plane, said injection orifice forms with said orthogonal direction at the first section plane a first feeding angle between -80 ° and + 80 ° and preferably between -60 ° and -30 °.

The absence of separation wall between the annular cavities of the ring sectors makes it possible to form a continuous annular cavity all around the circumference of the ring and thus to allow the generation and the circulation of a rotating flow of the air flow. cooling in the annular cavity of the ring.

The first feed angle directs the flow of injected cooling air through the ring support structure in a direction of rotation about the ring and not axially, that is, orthogonally to the circumferential or circular direction of the ring. This makes it possible to force and guide the flow of cooling air injected in the circumferential direction of the annular cavity and thus to promote the formation of a rotating flow.

In the state of the art, the impact plate attached directly to a metal ring makes it possible to increase the cooling very locally, while the rotary flow generated by the subject of the invention makes it possible to increase the cooling coefficient. global exchange in the annular cavity and thus improve the thermal profile of the ring. And without the need to use an extra room as an impact plate. This makes it possible to achieve a gain in mass as well as in manufacturing time.

According to a first aspect of the turbine ring assembly, in said first section plane, the orifice forms with the axial direction a second feed angle strictly greater than 0 ° and less than or equal to 30 °.

The second feed angle makes it possible to direct the flow of cooling air towards the annular cavity and thus to avoid interaction with the fastening lug facing the injection orifice. According to a second aspect of the turbine ring assembly, the ring support structure comprises a plurality of injection ports regularly distributed on the same circumference of the ring.

This makes it possible to have a better established rotary flow and thus a better homogeneity of the cooling of the ring.

According to a third aspect of the turbine ring assembly, each ring sector comprises at least one fluidic disturbance disposed on the outer face of the ring within the annular cavity.

The fluidic disturbance disposed in the annular cavity of a ring sector can create turbulence and thus increase the exchange coefficients with the ring.

In a variant of the third aspect of the turbine ring assembly, each ring sector comprises a plurality of fluidic disturbers distributed on the outer face of the ring within the annular cavity.

Another of the object proposes a turbomachine comprising a turbine ring assembly as defined above.

Yet another object proposes an aircraft comprising at least one turbomachine as defined above.

Brief description of the drawings.

The invention will be better understood on reading the following, by way of indication but without limitation, with reference to the accompanying drawings in which:

- Figure 1 is a schematic axial sectional view of a first embodiment of a turbine ring assembly according to the invention;

FIG. 2 is a schematic front view of the ring support structure of the turbine ring assembly of FIG. 1;

FIG. 3 is a schematic top view of the ring support structure of the turbine ring assembly of FIG. 1;

- Figure 4 is a schematic axial sectional view of a second embodiment of a turbine ring assembly according to the invention. Detailed description of embodiments

FIG. 1 shows a high pressure turbine ring assembly comprising a turbine ring 1 made of ceramic matrix composite material (CMC) and a metal ring support structure 3. The turbine ring 1 surrounds a set of blades rotary (not shown). The turbine ring 1 is formed of a plurality of ring sectors 10, FIG. 1 being a view in axial section defined by the axial direction of the turbine ring 1 marked by the arrow D _A and by the direction radial of the turbine ring 1 marked by the arrow DR.

Each ring sector 10 has, in a first plane

(denoted by I in FIG. 2) defined by the axial directions DA and radial D _R , a substantially shaped section of the Greek letter π reversed. The section comprises in fact an annular base 12 and upstream and downstream radial attachment tabs 14 and 16. The terms "upstream" and "downstream" are used herein with reference to the direction of flow of the gas stream in the turbine represented by arrow F in FIG. 1. The tabs of the ring sector 10 could have another shape, the section of the ring sector having a shape other than π, such as for example a k-shape.

The annular base 12 comprises, in the radial direction DR of the ring 1, an inner face 12a and an outer face 12b opposite to each other. The inner face 12a of the annular base 12 is coated with a layer 13 of abradable material forming a thermal and environmental barrier and defines a stream of flow of gas in the turbine.

The upstream and downstream radial hooking tabs 14 and 16 project in the direction DR from the outer face 12b of the annular base 12 away from the upstream and downstream ends 121 and 122 of the annular base 12. The upstream and downstream radial attachment tabs 14 and 16 extend over the entire width of the ring sector 10, that is to say over the entire arc described by the ring sector 10, or over the entire circumferential length of the ring sector 10.

The annular base 12 and the upstream and downstream latching lugs 14 and 16 of each ring sector 10 together form an annular cavity 120 open on a side opposite to the annular base 12 and at each circular end of the ring sector 10 , that is to say at each end of the ring sector 10 in contact with another ring sector 10 when the ring 1 is assembled. The ring 1 thus comprises an annular cavity in fluid communication over the entire circumference of the ring 1.

As illustrated in FIG. 1, the ring support structure 3 which is integral with a turbine casing comprises a central ring 31 having an axis of revolution coinciding with the axis of revolution of the turbine ring 1 when they are fixed together. The central ring 31 extends in the axial direction D _A of the ring 1 and in the circumferential direction of the ring 1. The ring support structure 3 further comprises an upstream annular radial flange 32 and a radial flange. annular downstream 36 which extend, in the radial direction D _R , from the central ring 31 to the center of the ring 1 and in the circumferential direction of the ring 1.

As illustrated in FIG. 1, the downstream annular radial flange 36 comprises a first free end 361 and a second end 362 integral with the central ring 31. The downstream radial annular flange 36 comprises a first portion 363 and a second portion 364, the first portion 363 extending between the first end 361 and the second portion 364, and the second portion 364 extending between the first portion 363 and the second end 362. The first portion 363 of the downstream annular radial flange 36 is at contact the downstream radial hooking tab 16. The second portion 364 is thinned relative to the first portion 363 so as to give some flexibility to the downstream annular radial flange 36 and thus not too much constrain the turbine ring 1 in CMC.

Similarly, the upstream annular radial flange 32 comprises a first free end 321 and a second end 322 integral with the central ring 31. The upstream radial annular flange 32 comprises a first portion 323 and a second portion 324, the first portion 323 extending between the first end 321 and the second portion 324, and the second portion 324 extending between the first portion 323 and the second end 322. The first portion 323 of the upstream radial annular flange 32 is in contact with the radial tab The second portion 324 is thinned with respect to the first portion 323 so as to give certain flexibility to the upstream annular radial flange 32 and thus not too much constrain the turbine ring 1 in CMC.

In the axial direction D _A , the downstream annular radial flange 36 of the ring support structure 3 is separated from the upstream annular radial flange 32 by a distance corresponding to the spacing of the upstream and downstream radial fastening tabs 14 and 16 so as to maintain the latter between the downstream annular radial flange 36 and the upstream annular radial flange 32.

The ring support structure 3 comprises, for each ring sector 10, an orifice 4 for injecting a flow of cooling air, represented by the arrow A, into the annular cavity 120. Each orifice 4 d injection is performed in the second portion 324 of the upstream annular radial flange 32.

Figures 2 and 3 show respectively a schematic front view and a schematic top view of the ring support structure 3 of the turbine ring assembly of Figure 1.

As illustrated in FIGS. 2 and 3, the injection orifice 4 has a non-orthogonal direction A with a second plane in which the upstream annular radial flange 32 extends, and not included in a third plane orthogonal to the plane in which extends the upstream annular radial flange 32. The second plane is defined by the radial direction D _R and a direction orthogonal to the first plane I. The orthogonal direction in the first plane I is indicated by the reference D _c and corresponding to the tangent to the circumferential direction of the ring at the intersection of the circumferential direction with the first section plane I. Thereafter the direction of orthogonal to the first section plane I is named tangential direction D _c . The third plane is defined by the tangential direction D _c and the axial direction D _A.

More precisely, as illustrated in FIG. 3, in the third plane, the injection orifice 4 forms, with the tangential direction D _c, a first feed angle α1 of between -80 ° and + 80 ° and preferably between -60 ° and -30 °. In the embodiment illustrated in FIGS. 2 and 3, the first feed angle ai has a value of 45 °.

The first feed angle ai initiates a direction to the flow of cooling air injected through the injection port 4 through the ring support structure 3 for inducing a circular flow in the annular cavity 120 to increase the overall exchange coefficient in the annular cavity and improve the thermal profile of the ring.

As illustrated in FIG. 1, in the first plane I defined by the radial direction D _R and the axial direction D _{A /} the injection orifice 4 forms with the axial direction D _A a second supply angle a ₂ strictly greater than 0 ° and less than or equal to 30 °.

The second feed angle ₂ makes it possible to direct the flow of cooling air towards the annular cavity 120 and thus to avoid interaction with the downstream fastening tab 16 and with the upstream fastening tab 14.

In Figure 4 is shown a schematic axial sectional view of a second embodiment of a turbine ring assembly according to the invention.

In this second embodiment, all the elements identical to the first embodiment illustrated in FIGS. 1 to 3 bear the same reference numerals.

The second embodiment differs from the first embodiment in that each ring sector 10 comprises a fluidic disturbance block 5 mounted on the outer face 12b of the ring 1 inside the annular cavity 120, that is to say between the upstream and downstream hooking tabs 14 and 16, to create turbulence and thus increase the exchange coefficients with the ring 1 for each ring sector 10.

A method of making a turbine ring assembly corresponding to that shown in FIG. 1 is now described.

Each ring sector 10 described above is made of ceramic matrix composite material (CMC) by forming a fibrous preform having a shape close to that of the ring sector and densification of the ring sector by a ceramic matrix .

For the production of the fiber preform, it is possible to use ceramic fiber yarns, for example SiC fiber yarns, such as those marketed by the Japanese company Nippon Carbon under the name "Hi-NicalonS", or carbon fiber yarns. . The fiber preform is advantageously made by three-dimensional weaving, or multilayer weaving with development of debonding zones to separate the preform portions corresponding to the tabs 14 and 16 of the sectors 10.

The weave can be interlock type, as illustrated. Other weaves of three-dimensional weave or multilayer can be used as for example multi-web or multi-satin weaves. Reference can be made to WO 2006/136755.

After weaving, the blank can be shaped to obtain a ring sector preform which is consolidated and densified by a ceramic matrix, the densification can be achieved in particular by chemical vapor infiltration (CVI) which is well known in itself. Alternatively, the textile preform can be a little hardened by CVI so that it is rigid enough to be manipulated, before raising liquid silicon by capillarity in the textile for densification ("Melt Infiltration").

A detailed example of manufacture of ring sectors in CMC is described in particular in document US 2012/0027572.

The ring support structure 3 is made of a metallic material such as a Waspaloy® alloy or inconel 718 or C263.

The realization of the turbine ring assembly is continued by mounting the ring sectors 10 on the ring support structure 3. For this, the ring sectors 10 are assembled together on an annular tool of the type. "Spider" comprising, for example, suckers configured to each hold a ring sector 10. The assembly of the ring sectors 10 is achieved by inserting intersector sealing tabs between each pair of ring sectors. The ring 1 is then mounted on the ring support structure 3 which comprises an injection orifice of a cooling air flow in the annular cavity for each ring sector 10.

The invention thus provides a turbine ring assembly comprising a ring of composite matrix ceramic material providing an injection of an air flow into the ring cavity suppressing the axial temperature gradient.

Claims

A turbine ring assembly comprising a plurality of ring sectors (10) of ceramic matrix composite material forming a turbine ring (1) and a ring support structure (3), each ring sector (10) having, in a first plane of section (I) defined by an axial direction (D _A ) and a radial direction (D _R ) of the turbine ring (1), an annular base portion (12) with in the radial direction (D _R ) of the turbine ring (1), an inner face (12a) defining the inner face of the turbine ring (1) and an outer face (12b) from which extend a first and a second attachment lugs (14, 16) defining between them a circumferentially open annular cavity (120), the ring support structure (3) having first and second radial lugs between which are maintained the first and second latching lugs (14, 16) of each ring sector (10), and at least one orifice ( 4) injecting a flow of cooling air into the annular cavity (120),

Characterized in that, in a second section plane comprising the axial direction (D _A ) of the ring (1) and a direction (D _c ) orthogonal to the first section plane (I), said injection port (4 ) forms with said direction (D _c ) orthogonal to the first section plane (I) a first feed angle (ai) between -80 ° and + 80 ° and preferably between -60 ° and -30 °.

2. The assembly of claim 1, wherein, in said first section plane, the injection port (4) forms with the axial direction (D _A ) a second feed angle (a ₂ ) strictly greater than 0 ° and less than or equal to 30 °.

3. Assembly according to one of claims 1 or 2, wherein the ring support structure (3) comprises a plurality of injection orifices (4) evenly distributed on the same circumference of the ring (1). .

4. Assembly according to one of claims 1 to 3, wherein each ring sector (10) comprises at least one fluidic disturbance disposed on the outer face (12b) of the ring (1) inside the annular cavity (120).

5. The assembly of claim 4, wherein each ring sector (10) comprises a plurality of fluidic disturbers distributed on the outer face (12b) of the ring (1) inside the annular cavity (120). .

A turbomachine comprising a turbine ring assembly (1) according to any one of claims 1 to 5.